EP0072134A1 - Spannvorrichtung für einen Antrieb - Google Patents

Spannvorrichtung für einen Antrieb Download PDF

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Publication number
EP0072134A1
EP0072134A1 EP82303909A EP82303909A EP0072134A1 EP 0072134 A1 EP0072134 A1 EP 0072134A1 EP 82303909 A EP82303909 A EP 82303909A EP 82303909 A EP82303909 A EP 82303909A EP 0072134 A1 EP0072134 A1 EP 0072134A1
Authority
EP
European Patent Office
Prior art keywords
belt
rotation
tensioning device
relative
shear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP82303909A
Other languages
English (en)
French (fr)
Inventor
Richard William Heater
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eaton Corp
Original Assignee
Eaton Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eaton Corp filed Critical Eaton Corp
Publication of EP0072134A1 publication Critical patent/EP0072134A1/de
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1227—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the viscous friction type, e.g. viscous fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/081—Torsion springs

Definitions

  • the present invention relates to drive tensioning systems, and more particularly, to tensioning devices for use with endless power transmission belts.
  • Such systems, and the belts used therein, are normally referred to by the term "serpentine", derived from the shape of the path which the belt follows.
  • Serpentine derived from the shape of the path which the belt follows.
  • the belt tensioner of the present invention may be used with . many types of chain and belt drive systems, it is especially advantageous when used with a serpentine belt drive system, anti will be described in connection therewith.
  • belt tensioners have included a first member which is fixed relative to the vehicle engine, and a second member which is rotatable relative to the first member.
  • the second member includes an idler pulley, or some other such device which engages the belt and transmits the tensioning force thereto.
  • the belt tensioner should operate in such a manner that the tensioner pulley always engages the belt with just the right amount of biasing force to maintain the nominal belt tension, for example, 150 lbs. This is especially difficult in the case of a serpentine system in which the various impulses and vibrations referred to above result in stretching and contracting of the belt, at varying, unpredictable frequencies, and at varying amplitudes.
  • the simplest form of prior art belt tensioner included merely an arrangement, such as a coil spring, for rotatably biasing the second member relative to the first, in an attempt to maintain a constant bias force of the tensioner pulley against the belt. See, for example, U.S. Pat. No. 3,374,686. It has been found, however, that if the frequency of any of the impulses and vibrations transmitted to the belt nearly matches one of the resonant frequencies of the spring, the spring will permit the tensioner pulley to separate from the belt, in response to outward movement of the belt, resulting in a serious slack condition of the belt.
  • a tensioning device including means for resisting and dampening impulses and vibrations transmitted by the belt to the tensioner.
  • a second major type of prior art belt tensioner included an elastomeric mass disposed between the first and second members. See, for example, U.S. Pat. No. 3,975,965.
  • one portion of the elastomeric mass is attached to the first member, and another portion is attached to the second member.
  • the tensioner in installed, the first and second members are displaced relative to each other, thus preloading the elastomer, so that the elastomer generates the initial bias against the belt, as well as resisting the impulses and vibrations transmitted by the belt.
  • tensioners are generally satisfactory.
  • a final type of prior art belt tensioner is exemplified by the unit produced commercially by Magna Industries, Inc. in which the first and second members each frictionally engage a relatively thin friction disc, made from a material such as a urethane plastic. It is a major disadvantage of such tensioners that the "static friction” (i.e., initial resistance to rotation of the second member) is relatively higher than the “dynamic friction” (i.e., resistance to rotation of the second member once it has begun to move). In addition, any change in the frictional engagement of the friction disc with either of the adjacent members will substantially alter the impulse and vibration dampening ability of the tensioner.
  • the resistance to movement is generally proportional to the frequency or velocity of the movement.
  • an improved belt tensioning device which comprises a first member fixedly mounted relative to the engine and defining a first axis of rotation and a second member mountea for rotation relative to the first member, about the first axis of rotation.
  • the second member includes a radially extending arm portion defining a second axis of rotation.
  • a tensioner pulley is rotatably mounted on the arm portion for rotation about the second axis of rotation, the pulley being adapted to engage the belt.
  • a biasing means includes a first portion seated relative to the first member and a second portion seated relative to the second member to bias the arm portion rotatably, relative to the first member, thereby biasing the tensioner pulley against the belt to create a nominal belt tension.
  • the first and second members define first and second annular surfaces which are closely spaced apart and cooperate to define a shear space therebetween.
  • the shear space is operable, in response to the presence of viscous fluid therein, to generate a viscous shear drag resisting rotation of the second member relative to the first member.
  • the viscous shear drag is generated as a function of the velocity of the rotation of the second member relative to the first member.
  • FIG. 1 illustrates a typical vehicle engine to which the present invention may be applied.
  • a V-6 automobile engine utilizing a serpentine belt 11 to transmit power from a crankshaft pulley 13 to a plurality of engine accessories.
  • these accessories are represented by a power steering pump pulley 15, an alternator pulley 17, an air conditioning compressor pulley 19, and a water pump pulley 21.
  • Each of the pulleys 13, 15, 17, 19, and 21 is suitably supported relative to the engine, and each is operatively connected to its associated component such that the belt 11 operates, in the subject embodiment, in a single, vertical plane.
  • a belt tensioning device is disposed between the pulley 15 and the pulley 17 and engages the belt 11 to provide the appropriate wrap-around on the pulleys 15 and 17.
  • the tensioning device 23 includes four major portions: a fixed portion 25; a rotatable portion 27; a biasing spring 29; and a tensioner (or idler) pulley 31.
  • the fixed portion 25 includes a generally annular plate member 33, including an annular rim 34, and which defines a central opening 35 and an axis of rotation 37.
  • a shaft member 39 Received within the opening 35 is a shaft member 39, including an integral shoulder portion 41.
  • the shaft member 39 terminates, adjacent the opening 35, in a stud portion 43, which extends through an opening defined by a bracket (shown in dottea lines in FIG. 4) attached to the engine.
  • orientation of the tensioning device 23 is achieved by means of a locating boss 44, which is received in another opening defined by the bracket.
  • the rotatable portion 27 includes a generally cylindrical housing 45, disposed about the shaft member 39.
  • the rotatable portion 27 also includes a radially extending arm portion 47 which, preferably, is formed integrally with the housing 45.
  • the arm portion 47 includes a forwardly-extending (down in FIG. 4), cylindrical boss portion 49 defining an axis of rotation 51.
  • the arm portion 47 also includes a rearwardly-extending stop portion 53, the function of which will be described subsequently.
  • the biasing spring 29 includes an end portion 55 received in a notch 57 defined by the rim 34.
  • the biasing spring 29 includes another end portion 59, which is seated against the stop portion 53, such that the spring 29 biases the arm portion 47 downward (in FIGS. 1 and 2).
  • the tensioner pulley 31 is disposea on the boss portion 49 for rotation about the axis 51. It should be noted that the tensioner pulley 31 engages the back side of the belt 11, i.e., the side opposite the V-notches, whereas the pulleys 13, 15, 17, and 19 all engage the side including the V-notches.
  • a pair of nylon sleeves 60 and 61 are disposed between the OD of the shaft member 39 and the ID of the housing 45. Disposed between the sleeves 59 and 61 is a rubber 0-ring 63, seated in a groove formed about the periphery of the shaft member 39. The function of the O-ring 63 will become apparent subsequently.
  • An annular disc-like member 65 is received on the forward end of the shaft member 39, and is fixedly attached thereto, such as by means of a rolled-over portion 67 of the shaft 39.
  • the housing 45 defines an annular chamber 69 which is concentric with the disc member 65.
  • the chamber 69 is sealed off by means of a cover member 71 and an 0-ring seal 73, with the housing 45 including a rolled-over portion 75, to retain the cover member 71, relative to the housing 45.
  • the space between the disk-like member 65 and the annular chamber 69 comprises a shear space which is filled with viscous fluid, preferably, a very high viscosity silicone fluid.
  • the shear space includes the space between the forward transverse surface of the member 65 and the adjacent surface of the cover 71; the space between the rearward transverse surface of the member 65 and the adjacent, transverse surface of the housing 45; and the space between the outer peripheral surface of the member 65 and the adjacent cylindrical surface defined by the housing 45.
  • FIG. 6 some of the advantageous properties of the present invention will be described in connection with the graph of resisting torque vs. frequency. It should be noted that, because the amplitude of movement of the tensioner pulley 31 is taken to be generally constant, the frequency of movement shown in the graph of FIG. 6 is indicative of the relative rotational velocity between the member 65 and housing 45, and therefore, is also indicative of the shear rate.
  • the graph of FIG. 6 represents the resisting torque, as a function of frequency, for the tensioning device shown in FIGS. 2-5 and is mathematically derived to indicate resisting torque resulting only from viscous shear drag, based upon known shear properties of silicone fluid.
  • the resisting torque shown in the graph of FIG. 6 does not take into account any resisting torque generated by mechanical friction, such as that resulting from the engagement of the housing 45 and the 0-ring seal 63.
  • the graph of FIG. 6 illustrates that the viscous shear drag, and resulting resisting torque, is generally proportional to the frequency (velocity) of movement of the respective shear surfaces.
  • the particular torque vs. frequency curve shown in FIG. b is for fluid having a viscosity of 100,000 centistokes.
  • resisting torque increases proportionately to minimize the chance of such separation.
  • resisting torque is proportional to the frequency (shear velocity), as well as to the fluid viscosity and to shear area. Therefore, it is believed to be within the ability to those skilled in the art to vary one or more of the factors listed above, to achieve the desired resisting torque for any given application.
  • FIGS. 7 and 8 there is illustrated an alternative embodiment of the present invention in which the shear area has been substantially increased, thereby making it possible to substantially decrease the fluid viscosity, while achieving the same resisting torque as in the previous embodiment.
  • like elements bear like numerals, while new or different elements bear numerals in excess of 80.
  • the shaft member 39 terminates, at its forward end, in a rectangular projection 81.
  • a plurality of annular plates 83 Disposed about the projection 81 is a plurality of annular plates 83, each of which defines a rectangular opening 85 through which the projection 81 passes.
  • the housing 45 includes a plurality of axial bores 87, and disposed in each bore 87 is a pin 89.
  • a plurality of annular plates 91 is in interleaved relationship with the plates 83, with each plate 91 defining a plurality of semicircular cutouts 93 to receive one of the pins 89 therein. Therefore, the plates 83 are rotatably fixed relative to the shaft 39, whereas the plates 91 are rotatably fixed relative to the housing 45.
  • the total shear area in the embodiment of FIGS. 7 and 8 is substantially greater than in the embodiment of FIG. 4 because the shear area in FIGS. 7 ana 8 includes the total area of overlap of each adjacent pair of plates 83 and 91, as well as the area of overlap between the forward-most plate 83 and the adjacent surface of the cover 71.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
EP82303909A 1981-08-03 1982-07-23 Spannvorrichtung für einen Antrieb Ceased EP0072134A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US28962681A 1981-08-03 1981-08-03
US289626 1981-08-03

Publications (1)

Publication Number Publication Date
EP0072134A1 true EP0072134A1 (de) 1983-02-16

Family

ID=23112342

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82303909A Ceased EP0072134A1 (de) 1981-08-03 1982-07-23 Spannvorrichtung für einen Antrieb

Country Status (2)

Country Link
EP (1) EP0072134A1 (de)
JP (1) JPS5865357A (de)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0087440A1 (de) * 1981-09-11 1983-09-07 Dayco Corp Bandspanner.
US4563167A (en) * 1982-09-29 1986-01-07 Dayco Corporation Belt tensioner and method of making the same
US4624652A (en) * 1982-06-25 1986-11-25 Dayco Corporation Belt tensioner, part therefor and methods of making the same
US4634408A (en) * 1981-09-11 1987-01-06 Dayco Corporation Belt tensioner, part therefor and methods of making the same
DE3528442C1 (de) * 1985-08-08 1987-01-15 Daimler Benz Ag Spannvorrichtung
US4708697A (en) * 1981-09-11 1987-11-24 Dayco Products, Inc. Belt tensioner, part therefor and methods of making the same
FR2609139A1 (fr) * 1986-12-27 1988-07-01 Koyo Seiko Co Dispositif de tension, notamment pour courroies de distribution de vehicules automobiles
FR2617556A1 (fr) * 1987-07-02 1989-01-06 Hutchinson Dispositif de tendeur rotatif pour courroie de transmission de puissance
US4934987A (en) * 1988-04-01 1990-06-19 Koyo Seiko Co., Ltd. Belt tensioner
DE4134354A1 (de) * 1991-10-17 1993-04-22 Schaeffler Waelzlager Kg Schwingungsdaempfer
GB2263150A (en) * 1991-12-18 1993-07-14 Ntn Toyo Bearing Co Ltd Belt tension adjusting device
EP0780597A1 (de) * 1995-12-18 1997-06-25 The Gates Corporation d/b/a/ The Gates Rubber Company Riemenspanner mit Dämpfungsmechanismus und Riementriebsystem
US5718649A (en) * 1996-02-16 1998-02-17 Dayco Products, Inc. Tensioner for a power transmission belt and method of making same
DE10127521A1 (de) * 2001-06-06 2002-12-12 Ina Schaeffler Kg Schwenklager für eine Spannvorrichtung
DE102004025738A1 (de) * 2004-05-26 2006-01-05 Ina-Schaeffler Kg Verbindungsanordnung zwischen einer Laufrolle und einer Spannvorrichtung sowie Verfahren zur Herstellung einer derartigen Verbindungsanordnung
WO2006117140A3 (de) * 2005-05-03 2007-03-22 Schaeffler Kg Verbindungsanordnung zwischen einer laufrolle und einer spannvorrichtung
DE102006035756A1 (de) * 2006-08-01 2008-02-28 Schaeffler Kg Umlenkrolleneinrichtung und Verfahren zur Herstellung derselben

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62188652U (de) * 1986-05-21 1987-12-01
JPS62258252A (ja) * 1986-04-30 1987-11-10 Koyo Seiko Co Ltd ベルト用オ−トテンシヨナ
JPH0792122B2 (ja) * 1986-12-27 1995-10-09 光洋精工株式会社 オ−トテンシヨナ
JPH0810020B2 (ja) * 1987-01-19 1996-01-31 日本精工株式会社 多板式流体粘性型オ−トテンシヨナ−
JPS63128353U (de) * 1987-02-13 1988-08-22
JPS63175342U (de) * 1987-05-02 1988-11-14
DE3824645A1 (de) * 1988-07-20 1990-01-25 Schaeffler Waelzlager Kg Spannvorrichtung
JPH0642123Y2 (ja) * 1988-10-18 1994-11-02 エヌティエヌ株式会社 オートテンショナ
JPH0480953U (de) * 1990-11-27 1992-07-14

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE359936C (de) * 1922-09-28 Heinrich Peters Einrichtung zum Daempfen der Schwingungen von Spannrollen an Riemen- oder Seiltrieben
FR1344080A (fr) * 1962-01-20 1963-11-22 Siemens Ag Dispositif pour transmettre un mouvement ou pour amortir le déplacement d'éléments mobiles l'un par rapport à l'autre
US3136170A (en) * 1962-12-26 1964-06-09 James J Murray Automatic tensioner
DE2608277A1 (de) * 1976-02-28 1977-09-01 Porsche Ag Spannvorrichtung fuer riemen, ketten oder dergleichen
US4270906A (en) * 1979-11-05 1981-06-02 Dyneer Corporation Belt tensioner construction

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE359936C (de) * 1922-09-28 Heinrich Peters Einrichtung zum Daempfen der Schwingungen von Spannrollen an Riemen- oder Seiltrieben
FR1344080A (fr) * 1962-01-20 1963-11-22 Siemens Ag Dispositif pour transmettre un mouvement ou pour amortir le déplacement d'éléments mobiles l'un par rapport à l'autre
US3136170A (en) * 1962-12-26 1964-06-09 James J Murray Automatic tensioner
DE2608277A1 (de) * 1976-02-28 1977-09-01 Porsche Ag Spannvorrichtung fuer riemen, ketten oder dergleichen
US4270906A (en) * 1979-11-05 1981-06-02 Dyneer Corporation Belt tensioner construction

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0087440A1 (de) * 1981-09-11 1983-09-07 Dayco Corp Bandspanner.
EP0087440B1 (de) * 1981-09-11 1986-10-15 Dayco Corporation Bandspanner
US4634408A (en) * 1981-09-11 1987-01-06 Dayco Corporation Belt tensioner, part therefor and methods of making the same
US4708697A (en) * 1981-09-11 1987-11-24 Dayco Products, Inc. Belt tensioner, part therefor and methods of making the same
US4624652A (en) * 1982-06-25 1986-11-25 Dayco Corporation Belt tensioner, part therefor and methods of making the same
US4563167A (en) * 1982-09-29 1986-01-07 Dayco Corporation Belt tensioner and method of making the same
DE3528442C1 (de) * 1985-08-08 1987-01-15 Daimler Benz Ag Spannvorrichtung
US4702727A (en) * 1985-08-08 1987-10-27 Daimler-Benz Aktiengesellschaft Tensioning device
FR2609139A1 (fr) * 1986-12-27 1988-07-01 Koyo Seiko Co Dispositif de tension, notamment pour courroies de distribution de vehicules automobiles
EP0300858A1 (de) * 1987-07-02 1989-01-25 Hutchinson Rotationsriemenspanner für Riemengetriebe
FR2617556A1 (fr) * 1987-07-02 1989-01-06 Hutchinson Dispositif de tendeur rotatif pour courroie de transmission de puissance
US4934987A (en) * 1988-04-01 1990-06-19 Koyo Seiko Co., Ltd. Belt tensioner
DE4134354A1 (de) * 1991-10-17 1993-04-22 Schaeffler Waelzlager Kg Schwingungsdaempfer
GB2263150A (en) * 1991-12-18 1993-07-14 Ntn Toyo Bearing Co Ltd Belt tension adjusting device
GB2263150B (en) * 1991-12-18 1996-02-28 Ntn Toyo Bearing Co Ltd Belt tension adjusting device
EP0780597A1 (de) * 1995-12-18 1997-06-25 The Gates Corporation d/b/a/ The Gates Rubber Company Riemenspanner mit Dämpfungsmechanismus und Riementriebsystem
US5718649A (en) * 1996-02-16 1998-02-17 Dayco Products, Inc. Tensioner for a power transmission belt and method of making same
DE10127521A1 (de) * 2001-06-06 2002-12-12 Ina Schaeffler Kg Schwenklager für eine Spannvorrichtung
DE102004025738A1 (de) * 2004-05-26 2006-01-05 Ina-Schaeffler Kg Verbindungsanordnung zwischen einer Laufrolle und einer Spannvorrichtung sowie Verfahren zur Herstellung einer derartigen Verbindungsanordnung
WO2006117140A3 (de) * 2005-05-03 2007-03-22 Schaeffler Kg Verbindungsanordnung zwischen einer laufrolle und einer spannvorrichtung
DE102006035756A1 (de) * 2006-08-01 2008-02-28 Schaeffler Kg Umlenkrolleneinrichtung und Verfahren zur Herstellung derselben

Also Published As

Publication number Publication date
JPS5865357A (ja) 1983-04-19

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Inventor name: HEATER, RICHARD WILLIAM